US6869067B2 - Sheath for a suspension spring - Google Patents

Sheath for a suspension spring Download PDF

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Publication number
US6869067B2
US6869067B2 US10/461,325 US46132503A US6869067B2 US 6869067 B2 US6869067 B2 US 6869067B2 US 46132503 A US46132503 A US 46132503A US 6869067 B2 US6869067 B2 US 6869067B2
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US
United States
Prior art keywords
centering
sheath
bearing
tabs
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US10/461,325
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English (en)
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US20040094879A1 (en
Inventor
Philippe Duval
Roger Henri
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sogefi Suspensions SA
Original Assignee
Allevard Rejna Autosuspensions SA
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Application filed by Allevard Rejna Autosuspensions SA filed Critical Allevard Rejna Autosuspensions SA
Assigned to ALLEVARD REJNA AUTOSUSPENSIONS reassignment ALLEVARD REJNA AUTOSUSPENSIONS ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DUVAL, PHILIPPE, HENRI, ROGER
Publication of US20040094879A1 publication Critical patent/US20040094879A1/en
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Publication of US6869067B2 publication Critical patent/US6869067B2/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/024—Covers or coatings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • F16F1/12—Attachments or mountings
    • F16F1/126—Attachments or mountings comprising an element between the end coil of the spring and the support proper, e.g. an elastomeric annulus
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/12—Mounting of springs or dampers
    • B60G2204/124—Mounting of coil springs
    • B60G2204/1242—Mounting of coil springs on a damper, e.g. MacPerson strut
    • B60G2204/12422—Mounting of coil springs on a damper, e.g. MacPerson strut anchoring the end coils on the spring support plate

Definitions

  • the present invention relates to a spring suspension system comprising a helical spring, a sheath, and at least one centering and bearing cup, said spring having an end turn with at least a fraction thereof covered by said sheath and centered and bearing on said centering and bearing cup.
  • the invention applies in particular to the field of motor vehicles.
  • the presence of a sheath surrounding at least a fraction of the last turn of the spring serves to avoid the spring making direct contact with the cup. Consequently, the noise coming from the end turn rubbing against the cup is attenuated and the vibration which can be transmitted to the rest of the vehicle is damped.
  • the sheath serves to protect the end turn of the spring, in particular against corrosion which can arise in the vicinity of the contact between the end turn and the cup due to water and/or debris accumulating.
  • Spring suspension systems of this type comprising a tubular sheath covering the entire section of at least a fraction of the end turn. Nevertheless, such sheaths encourage water to condense, which can then penetrate inside the tube of the sheath and generally gives rise to corrosion of the turn. In addition, such a sheath is lengthy to mount since it needs to be threaded on via one of its ends.
  • spring suspension systems of this type comprising a sheath which presents an opening that enables the sheath to be fitted easily over the turn, while simultaneously avoiding water condensing around the entire section of the turn. Nevertheless, water and/or debris can accumulate in the bottom of the sheath, in particular for a bottom cup where the opening faces towards the top of the suspension system, and that leads to the turn being corroded.
  • the object of the invention is to provide a spring suspension system having a sheath that is easy to mount and that allows water and debris to be evacuated naturally.
  • the opening of the sheath facing towards the inside of the end turn makes it easier to put the sheath into place on the turn, which in addition does not tend to become separated therefrom.
  • the device presents spacer means preferably situated locally between the sheath and the centering and bearing cup.
  • spacer means preferably situated locally between the sheath and the centering and bearing cup.
  • the presence of the spacer means makes it possible to localize accurately the points of contact between the sheath and the centering and bearing cup.
  • the spacer means may be fitted to the cup and/or the sheath, for example by being overmolded thereon, or indeed the spacer means and the sheath may form portions of a single sheath-and-spacer piece.
  • sheath-and-spacer piece needs to be adapted to the intended function (localized bearing, off-centering, right or left directions, etc . . . ), while the remainder of the device, and in particular the spring and the centering and bearing cup are standard.
  • said spacer means comprise radial spacer means suitable for holding the sheath at a distance from a centering face of the centering and bearing cup.
  • the radial spacer means comprise centering tabs extending between the sheath and the centering face of the centering and bearing cup.
  • radial spacer means it suffices to change the shape of the radial spacer means to change the centering of the sheath relative to the centering and bearing cup, and thus to change the centering of the spring.
  • radial spacer means When the radial spacer means are formed on the sheath, a single type of spring can be off-center to a greater or lesser extent, depending on the type of sheath which covers its end turn.
  • the spacer means comprise axial spacer means suitable for holding the sheath at a distance from the bearing face of the centering and bearing cup.
  • the axial spacer means comprise bearing tabs extending between the sheath and the bearing face of the centering and bearing cup.
  • the sheath is raised or lowered relative to the bearing face of the bottom or top centering and bearing cup, thereby making it correspondingly easier for water and debris to be evacuated.
  • the bearing tabs may be located differently from one suspension system to another in order to confer differing properties thereto (right or left suspensions for a vehicle, etc.).
  • the spacer means may comprise both radial spacer means and axial spacer means.
  • a centering tab and a bearing tab may optionally be superposed one above the other in the axial direction of the spring, thereby optionally forming a pair of centering and bearing tabs.
  • FIG. 1 is a perspective view of a sheath of the invention
  • FIG. 2 is a section view on arrows II-II in FIG. 1 showing the sheath disposed on a centering and bearing cup;
  • FIG. 3 is a plan view seen looking along direction III of FIG. 1 ;
  • FIG. 4A is a section view on arrows IVA-IVA of FIG. 3 showing a variant sheath disposed on a centering and bearing cup;
  • FIG. 4B is a section view on arrows IVB-IVB of FIG. 3 , showing a variant of the spacer means;
  • FIG. 4C is a section view on arrows IVC-IVC of FIG. 3 showing another variant of the spacer means.
  • FIG. 5 is a fragmentary section view of a variant sheath placed on a centering and bearing cup.
  • FIG. 1 shows a sheath 10 for covering at least a fraction of an end turn of a spring (drawn in chain-doted lines in FIG. 1 ), the sheath presenting an opening 12 that extends around the inner periphery 14 of the sheath 10 .
  • the opening 12 is preferably substantially longitudinal and occupies the entire length L of said sheath 10 .
  • the sheath 10 When the sheath 10 is placed on the end turn, it takes up a shape that is substantially helical.
  • the sheath 10 is very easily mounted on a helical spring 16 in a spring suspension system by taking care to turn the opening 12 towards the axis X R of the spring, as shown in FIG. 2 . It suffices to snap-fasten the sheath 10 onto the spring 16 in the vicinity of that fraction of the end turn 16 ′A that is to be covered, in order to ensure that the sheath is positioned and remains in place. Since the opening 12 faces towards the axis X R of the spring, the sheath 10 has a natural tendency to remain placed on the spring 16 surrounding the end turn 16 A.
  • Spacer means which are preferably formed directly on the sheath 10 so as to constitute a single sheath and spacer piece 11 , e.g. made by molding or injection of plastic material, elastomer, etc., enable the fraction of the end turn 16 ′A that is covered by the sheath 10 to be centered on and to bear against a centering and bearing cup 18 (see FIG. 2 ).
  • the spacer means comprise firstly radial spacer means 20 suitable for holding the sheath 10 at a distance from a centering face 22 of the centering and bearing cup 18 , and secondly axial spacer means 24 suitable for holding the sheath 10 at a distance from a bearing face 26 of the centering and bearing cup 18 .
  • the radial spacer means 10 extend between the sheath 10 and the centering face 22 of the centering and bearing cup 18 .
  • These centering tabs 20 are advantageously formed directly on the sheath 10 and are turned towards the axis X R of the spring 16 in such a manner as to bear against the centering face 22 whose axis of symmetry X C coincides with said axis X R , such that centering takes place radially around the axis X R of the spring 16 (or the axis X R of the centering and bearing cup 18 ).
  • the axial spacer means 24 extend between the sheath 10 and the bearing face 26 of the centering and bearing cup 18 .
  • these bearing tabs 24 may be distributed to a greater or lesser extent around the inner periphery 14 of the sheath 10 .
  • bearing takes place substantially parallel to the axis X R of the spring 16 .
  • these bearing tabs 24 may present respective transverse extensions 28 in the vicinity of an end 10 A of the sheath 10 , said transverse extensions being suitable for co-operating with the centering face 22 so as to form a centering and bearing tab 30 .
  • This transverse extension 28 is analogous to a centering tab 20 , such that the centering and bearing tabs 30 serve simultaneously to hold the sheath 10 apart from the centering face 22 and from the bearing face 26 .
  • At least one of the centering tabs 20 and one of the bearing tabs 24 are preferably superposed in an axial direction of the spring 16 so as to form a centering and bearing tab pair 32 occupying both sides of the opening 12 .
  • the centering and bearing cup 18 is a bottom cup, as shown in FIG. 2 , then the centering tab 20 is placed above the bearing tab 24 .
  • the opposite configuration is adopted when the centering and bearing cup is a top cup.
  • cup being described is a bottom cup so that terms like “beneath” and “bottom” relate to a zone closer to the bearing face of the centering and bearing cup. It follows that the elements described are the same for a centering and bearing cup that is a top cup, but in a configuration that is the opposite way up.
  • the sheath shown in FIG. 1 has two centering and bearing tab pairs 32 occupying opposite sides of the opening 12 , and located at respective opposite ends 10 A and 10 B of the sheath.
  • At least one of the centering tabs 20 is disposed above another centering tab 20 in an axial direction of the spring 16 so as to form a pair of centering tabs 34 extending on either side of the opening 12 .
  • each of the centering tabs 20 and of each of the bearing tabs 24 is a curvilinear length l lying in the range 4 millimeters (mm) to 40 mm, and preferably in the range 8 mm to 15 mm.
  • centering tabs 20 and of the centering and bearing tabs 30 are preferably matched to the outline of the centering face 22 against which they come to bear.
  • the centering tabs 20 and the centering and bearing tabs 30 may present curvature C analogous to the curvature of the centering face 22 .
  • the centering zone 36 of the sheath 10 i.e. on each of the centering tabs 20 and on each of the centering and bearing tabs 30 , may present a slope P relative to the axis X C that is analogous to the slope P 22 at which the centering face 22 is inclined.
  • the centering face 22 ′ of a centering and bearing cup 18 ′ extends substantially parallel to the axis X of the spring 16 , as shown in FIG. 4A , the slope P′ of the centering zone 36 ′ of each centering tab 20 ′ and of each centering and bearing tab 30 ′ is nil since the slope P 22′ of the centering face 22 ′ is nil.
  • the centering zone 36 ′ of the sheath 10 ′ is substantially parallel to the axis X C
  • the centering face 22 ′ at the bearing face 26 ′ of the centering and bearing cup 18 is substantially transverse.
  • centering tabs 20 , the bearing tabs 24 , and the centering and bearing tabs 30 may be spaced differently from one sheath to another, depending on the type of suspension system that is desired, and this applies regardless of the type of centering and bearing cup involved.
  • the number N 24 of bearing tabs 24 and the number N 20 of centering tabs 20 are preferably both in the range 2 to 20, so that the curvilinear spacing between two successive tabs around the turn enables the spring to be centered and to bear in stable manner against the centering and bearing cup.
  • the cross-section 10 C of the sheath 10 is preferably C-shaped with the opening 12 of the C-shape facing towards the inside of the end turn 16 A, i.e. towards the axis X R of the spring 16 .
  • the width of the gap I which corresponds to the distance between the sheath and the centering face of the cup is advantageously not less than 2 mm and preferably lies in the range 4 mm to 10 mm.
  • the height of the gap J corresponding to the distance between the sheath and the bearing face of the cup is advantageously not less than 2 mm and may increase along the turn because of the slope of the turn relative to the bearing face.
  • the length of the centering tabs and the length of the transverse extensions may either be constant from one tab to the next, or on the contrary may vary in order to enable the end turn 16 A to be off-center.
  • the length L 20 of the centering tabs 20 and the length L 28 of the transverse extensions 28 is constant from one tab to another.
  • the centering and bearing cup 18 ′ presents a centering face 22 ′ parallel to the axis X R of the spring 16
  • the length L 20 of the centering tabs 20 and the length L 28 of the transverse extensions 28 are constant from one tab to another (L 20 is substantially equal to L 28 ).
  • the length L 20 ′ of the centering tabs 20 ′ and the length L 28′ of the transverse extensions 28 ′ varies from one type of tab to the other with the tabs situated on the side where the eccentricity is positive being shorter than the others.
  • the top centering tab 20 ′ situated in the vicinity of the end 10 ′A of the turn 16 is shorter than the centering tab 120 ′ situated in the vicinity of the end 10 ′B (L 20′ ⁇ L 120′ ).
  • the transverse extensions 28 ′ and 128 ′ respectively situated in the vicinity of the end 10 ′A and in the vicinity of the end 10 ′B.
  • the bearing tabs 24 ′, and more particularly the centering and bearing tabs 30 ′ are of respective thicknesses that increase between successive tabs on going away from the bearing face 26 following the end turn 16 A.
  • the bottom tabs may be of different types.
  • the bottom centering tabs may bear against the bearing face 26 ′ of the centering and bearing cup 18 ′ so as to form a centering and bearing tab 30 ′ or 130 ′ which, in combination with a top centering tab 20 ′, forms a centering and bearing pair of tabs 32 ′ or 132 ′, as shown in FIG. 4 A.
  • the centering and bearing tab 30 ′ may be a single piece (right-hand side of FIG. 4 A), for example beside the nearer side of the centering and bearing cup 18 ′, in particular in the vicinity of the end 10 ′A, or it may be shaped to avoid any risks of excessive friction between the sheath 10 ′ and the centering and bearing tabs 18 ′ and to save on the amount of material used.
  • extension 128 ′ when the extension becomes too thick to compensate for the height difference of the end turn 16 ′A, provision can be made for said extension 128 ′ to be solely in a shape analogous to a centering tab 20 ′, so that the bearing tab 124 ′ does not come directly into contact with the centering face 22 ′, but only via said extension 128 ′; the bearing area of the bearing zone 36 ′ is thus greatly limited.
  • the centering and bearing tab 130 ′ close to the remoter end 10 ′B of the bearing face 26 ′ of the centering and bearing cup 18 ′ is formed by two branches constituting respectively the bearing tab 124 ′ and the centering tab 128 ′, a gap being left between the bearing tab 124 ′ and the centering face 22 ′, and between the centering tab 128 ′ and the bearing face 26 ′ (left-hand side of FIG. 4 A), whereas this gap does not exist for the centering and bearing tab 30 ′.
  • the bottom centering tabs need bear against only the centering face 22 ′, as shown in FIG. 4B , thereby forming a pair of centering tabs 34 ′.
  • the bottom tab may be formed solely by a bearing tab 224 ′ of thickness e 224 , increasing with increasing distance of the tab from the bearing face 26 ′ of the centering and bearing cup 18 ′.
  • a centering tab 20 ′ may be disposed above said bottom bearing tab 224 ′, as shown in FIG. 4 C.
  • the centering and bearing cup 18 has a centering face 22 that is inclined.
  • the two centering and bearing tabs 30 forming a single piece present thicknesses e 30 that differ from one tab to the other, so as to compensate for the difference in height of the end turn 16 A (shown in chain-doted lines) from one end 10 A to the other 10 B.
  • the thickness e 30 of the centering and bearing tab 30 at the end 10 B of the sheath 10 is greater than the thickness e 30 of the centering and bearing tab 30 at the opposite end 10 A of the sheath 10 .
  • FIG. 5 shows another variant of a sheath 10 ′′ which comprises, for a bottom centering and bearing cup, bottom centering and bearing tabs 30 ′′ that are not disposed beneath a top centering tab.
  • These centering and bearing tabs 30 ′ distributed around the sheath 10 ′′ may present varying shapes and thicknesses from one centering and bearing tab to another depending on distance from the end turn 16 A, and in particular the centering zone 36 ′′ and the opening 12 ′′ may be of different shapes from one sheath 10 ′′ to another or on a given sheath 10 ′′, so as to center the spring in different manners relative to the centering face 22 , and/or so as to have differ spacings relative to the bearing face 26 .
  • This type of sheath 10 ′′ that does not present a top centering tab placed above a centering and bearing tab 30 ′′ serves to limit the amount of debris and water that penetrates into the vicinity of the tab 30 ′′, and care is taken to ensure that the curvilinear width of these centering and bearing tabs 30 ′′ is shorter. Consequently, any debris which does accumulate locally is easily removed from each side of each of said centering and bearing tabs 30 ′′ between the sheath 10 ′′ and the cup 18 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Springs (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Damping Devices (AREA)
  • Closures For Containers (AREA)
US10/461,325 2002-06-13 2003-06-13 Sheath for a suspension spring Expired - Lifetime US6869067B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0207292A FR2840966B1 (fr) 2002-06-13 2002-06-13 Gaine pour ressort de suspension
FR0207292 2002-06-13

Publications (2)

Publication Number Publication Date
US20040094879A1 US20040094879A1 (en) 2004-05-20
US6869067B2 true US6869067B2 (en) 2005-03-22

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US10/461,325 Expired - Lifetime US6869067B2 (en) 2002-06-13 2003-06-13 Sheath for a suspension spring

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US (1) US6869067B2 (de)
EP (1) EP1375955B1 (de)
JP (1) JP4467912B2 (de)
AT (1) ATE358245T1 (de)
DE (1) DE60312774T2 (de)
ES (1) ES2285060T3 (de)
FR (1) FR2840966B1 (de)

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US20060131119A1 (en) * 2004-12-16 2006-06-22 Showa Corporation Spring sheet structure of hydraulic shock absorber
US20060145403A1 (en) * 2004-12-16 2006-07-06 Satoshi Oohashi Spring spacer for a spring
US20080224369A1 (en) * 2005-10-13 2008-09-18 Renault S.A.S. Sheathing for a Suspension Spring
US20100147919A1 (en) * 2008-12-17 2010-06-17 Hilti Aktiengesellschaft Hand-held drive-in tool
US20100252971A1 (en) * 2009-04-02 2010-10-07 Dong Yang Physical & Chemical Protective tube for coil spring of vehicle suspension device
US20110204551A1 (en) * 2010-02-24 2011-08-25 Honda Motor Co., Ltd. Spring guide and cushion device
RU2508999C2 (ru) * 2011-05-10 2014-03-10 Евгений Иванович Андряков Сегментная изолирующая прокладка пружины (варианты)
US20140230222A1 (en) * 2011-11-16 2014-08-21 Newfrey Llc Spring retainer clip
US20170184171A1 (en) * 2015-12-27 2017-06-29 Daimler Chu Shock absorber spring retention structure of remote control car
US20180027976A1 (en) * 2015-02-28 2018-02-01 Grandi-One Furniture Co., Ltd. Spring bed with quick assembly and disassembly
US20220105766A1 (en) * 2020-10-01 2022-04-07 Subaru Corporation Suspension

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DE102005050024B4 (de) * 2005-10-19 2007-11-22 Zf Friedrichshafen Ag Federteller, insbesondere für einen Schwingungsdämpfer
JP5198784B2 (ja) * 2007-03-29 2013-05-15 ボッシュ株式会社 コイルスプリングの防振機構およびこれを用いた倍力装置
FR2919034B1 (fr) * 2007-07-20 2012-05-04 Woco Avs Sas Systeme ressort-coupelle de suspension
FR2918927A1 (fr) * 2007-07-20 2009-01-23 Allevard Rejna Autosuspensions Suspension de vehicule automobile a ressort protege contre la corrosion.
DE102009057516B4 (de) 2008-12-11 2016-06-02 Franz Xaver Hamann Einbauteil einer Fahrwerksfederung in der Form eines Fortsatzes einer Schrauben- bzw. Spiralfeder sowie eine entsprechende Fahrwerkfederung und ein dazugehöriges Höhenniveauregulierungsverfahren
WO2011118390A1 (ja) * 2010-03-23 2011-09-29 本田技研工業株式会社 サスペンション装置
JP2012001162A (ja) * 2010-06-18 2012-01-05 Chuo Spring Co Ltd 懸架装置
US8448962B2 (en) 2010-08-26 2013-05-28 General Electric Company Systems and methods providing variable spring stiffness for weight management in a rail vehicle
JP5877068B2 (ja) * 2012-01-05 2016-03-02 本田技研工業株式会社 スプリングシート
JP5646023B2 (ja) * 2013-03-12 2014-12-24 株式会社ショーワ 弾性体シート及びサスペンション装置
EP3260729B1 (de) * 2015-02-17 2021-03-31 NHK Spring Co., Ltd. Unterseitiges federaufnahmeelement
JP6463200B2 (ja) * 2015-03-31 2019-01-30 Ｋｙｂ株式会社 スプリングガイド及びサスペンション装置
CN108368907B (zh) * 2015-12-10 2021-07-09 巴斯夫欧洲公司 用于螺旋弹簧的弹簧支架
JP2020125814A (ja) * 2019-02-05 2020-08-20 中央発條株式会社 懸架装置用ばね
JP7332560B2 (ja) * 2020-09-25 2023-08-23 トヨタ自動車株式会社 リアサスペンションとそのコイルスプリング

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US2815201A (en) * 1954-02-17 1957-12-03 Ferroviaires Soc Elastic device
US2832587A (en) * 1955-06-06 1958-04-29 Universal Air Lift Inc Spring booster assemblies
FR1308763A (fr) 1960-10-26 1962-11-09 Gomma Antivibranti Applic Bague antivibrante en caoutchouc pour suspensions à ressort à boudin, en particulier pour véhicules automobiles
US4721325A (en) * 1986-11-19 1988-01-26 General Motors Corporation Suspension strut with quick take-apart upper mount
US4732372A (en) * 1984-08-20 1988-03-22 Budd Company Dampers for mechanical railway springs
FR2656052A1 (fr) 1989-12-14 1991-06-21 Allevard Ind Sa Ressort helicouidal de suspension automobile equipe d'un dispositif antibruit.
US5299786A (en) 1993-03-17 1994-04-05 Freudenberg-Nok General Partnership Noise suppression member
EP0791491A1 (de) 1996-02-23 1997-08-27 Ateliers Métallurgiques de Saint Urbain (AMSU) Radaufhängung mit Schraubenfeder
US6293572B1 (en) * 1997-12-16 2001-09-25 Daimlerchrysler Corporation Isolated support for a rear suspension component 1

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2815201A (en) * 1954-02-17 1957-12-03 Ferroviaires Soc Elastic device
US2832587A (en) * 1955-06-06 1958-04-29 Universal Air Lift Inc Spring booster assemblies
FR1308763A (fr) 1960-10-26 1962-11-09 Gomma Antivibranti Applic Bague antivibrante en caoutchouc pour suspensions à ressort à boudin, en particulier pour véhicules automobiles
US4732372A (en) * 1984-08-20 1988-03-22 Budd Company Dampers for mechanical railway springs
US4721325A (en) * 1986-11-19 1988-01-26 General Motors Corporation Suspension strut with quick take-apart upper mount
FR2656052A1 (fr) 1989-12-14 1991-06-21 Allevard Ind Sa Ressort helicouidal de suspension automobile equipe d'un dispositif antibruit.
US5299786A (en) 1993-03-17 1994-04-05 Freudenberg-Nok General Partnership Noise suppression member
EP0791491A1 (de) 1996-02-23 1997-08-27 Ateliers Métallurgiques de Saint Urbain (AMSU) Radaufhängung mit Schraubenfeder
US6293572B1 (en) * 1997-12-16 2001-09-25 Daimlerchrysler Corporation Isolated support for a rear suspension component 1

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060145403A1 (en) * 2004-12-16 2006-07-06 Satoshi Oohashi Spring spacer for a spring
US7527252B2 (en) * 2004-12-16 2009-05-05 Yamaha Hatsudoki Kabushiki Kaisha Spring spacer for a spring
US7806392B2 (en) * 2004-12-16 2010-10-05 Showa Corporation Spring sheet structure of hydraulic shock absorber
US20060131119A1 (en) * 2004-12-16 2006-06-22 Showa Corporation Spring sheet structure of hydraulic shock absorber
US20080224369A1 (en) * 2005-10-13 2008-09-18 Renault S.A.S. Sheathing for a Suspension Spring
US20100147919A1 (en) * 2008-12-17 2010-06-17 Hilti Aktiengesellschaft Hand-held drive-in tool
US20100252971A1 (en) * 2009-04-02 2010-10-07 Dong Yang Physical & Chemical Protective tube for coil spring of vehicle suspension device
US8740198B2 (en) * 2010-02-24 2014-06-03 Honda Motor Co., Ltd. Spring guide and cushion device
US20110204551A1 (en) * 2010-02-24 2011-08-25 Honda Motor Co., Ltd. Spring guide and cushion device
RU2508999C2 (ru) * 2011-05-10 2014-03-10 Евгений Иванович Андряков Сегментная изолирующая прокладка пружины (варианты)
US20140230222A1 (en) * 2011-11-16 2014-08-21 Newfrey Llc Spring retainer clip
US9586453B2 (en) * 2011-11-16 2017-03-07 Newfrey Llc Spring retainer clip
US20180027976A1 (en) * 2015-02-28 2018-02-01 Grandi-One Furniture Co., Ltd. Spring bed with quick assembly and disassembly
US10582777B2 (en) * 2015-02-28 2020-03-10 Grandi-One Furniture Co., Ltd. Spring bed with quick assembly and disassembly
US20170184171A1 (en) * 2015-12-27 2017-06-29 Daimler Chu Shock absorber spring retention structure of remote control car
US9714688B2 (en) * 2015-12-27 2017-07-25 Daimler Chu Shock absorber spring retention structure of remote control car
US20220105766A1 (en) * 2020-10-01 2022-04-07 Subaru Corporation Suspension
US11865886B2 (en) * 2020-10-01 2024-01-09 Subaru Corporation Suspension

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FR2840966B1 (fr) 2004-10-15
EP1375955B1 (de) 2007-03-28
DE60312774D1 (de) 2007-05-10
JP4467912B2 (ja) 2010-05-26
EP1375955A1 (de) 2004-01-02
FR2840966A1 (fr) 2003-12-19
JP2004162901A (ja) 2004-06-10
ATE358245T1 (de) 2007-04-15
US20040094879A1 (en) 2004-05-20
ES2285060T3 (es) 2007-11-16
DE60312774T2 (de) 2007-12-06

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